Grinding machinery



July 2, 1935. F. s. HAAS 2,006,570

GRINDING MACHINERY Filed July 28, 1931 3 Sheets-Sheet 1 Zhmentor K Gttorneg July 2, F. 5 HAA 2,006,570

GRINDING MACHINERY Filed July 28, 1931 5 Sheets-Sheet 2 i (Ittorneg July 2, 1935. F, s, HAA 2,000,570

GRINDING MACHINERY Filed July 28, 1931 5 Sheets-Sheet 3 r attorney Patented July 2, 1935 UNITED STATES PATENKTYOFFICE 2,006,570 GRINDING MACHINERY Frederick S. Haas, Cincinnati, Ohio, assignor to Cincinnati Grinders Incorporated, Cincinnati, Ohio, a corporation of Ohio. v Application July 28, 1931, Serial No. 553,490 17 Claims. ('01. 51-403 This invention relates to improvements in grinding machines and especially to improvements in a mechanism for reciprocating the grinding wheel and its spindle.

An object of the invention is the provision of improved means for reciprocating a grinding wheel and its spindle relative to the work piece to break up grinding lines and the like on the work. 1

Another object of the invention'is the provision of a reciprocating mechanism that may be varied as to the rate of reciprocation during the grinding operation.

A further object of the invention is the provision of improved means cooperating with the spindle reciprocato-r for effecting such reciprocation at a predetermined point in the grinding cycle.

A still further object of the invention is the provision of a grinding wheel spindle reciprocator for use with centerless grinders including im proved operating means for the reciprocator adapted to operate in'timed sequence with the rotation of certain parts of the grinder, such as the regulating wheel thereof. o

Other objects and advantages of the present invention should be readily apparent by reference to the following specification considered in conjunction with the accompanying drawings and it is to be understood that any modifications may be made in the exact structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention.

In the drawings: 7

Figure 1 is an elevational view of a centerless grinder embodying the improvements of this in- Vention.

Figure 2 is a plan view of the machine shown in Figure 1.

Figure 3 is a sectional view through the spindle reciprocator taken on line 33 of Figure 2.

Figure 4 is a sectional view through the control mechanism for the reciprocator, as seen from line 4-4013 Figure2.

Figure 5 is a sectional view taken at right angles to Figure l, as seen from line 5-5 of Figure 2.

Figure 6 is an elevational view of the regulating wheel used with the grinder illustrated in Figure 1. v

Figure '7 is a horizontal section through the throat of a centerless grinder taken on line 1-1 of Figure l.

Figure 8 is a sectional View taken on line 88 of Figure 7,

Throughout the several views of the drawings similar reference characters are employed to denote the same or similar parts.

While the invention has been illustrated and described in connection with a centerless grinder, it is tube understood that it may used with equal facility with'other types of grinding machines or machine tools requiring a relative reciprocation between the work and tool. The particular device illustrated in the drawings may comprise a bed l having rising therefrom the pedestal bearing ll in'which is journaled the spindle l2 for "the grinding wheel I3. The spindle l2 is driven by any suitable or desirable means at a high rate of speed to properly effect a stock removal by the grinding wheel Hi. The bed Ill is further provided with ways M on which is slidably reciprocable a slide l in turn having ways for an upper slide lfisupporting the housing or head I] in. which is journaled a spindle l8 for the regulating wheel I9. The spindle; l8 and regulating wheel l9 are rotatedat a relatively slow rate of speed to frictionally engage and rotate a work piece while-in grinding engagement with the grinding wheel I3. The proximate points of the wheels are spaced from one another a predetermined distanceuto form the grinding throat in which the work is positioned during the grinding operation, being supported by a work rest blade 20 which subtends the grinding throat. At this point it may be noted that the operative faces of the grinding and regulating wheels travel in opposite directions as respects the work rest blade whereby the grinding wheel travels downwardly so that the blade takes the grinding thrust thereof while the regulating wheel travelsin an upwardly direction properly rotating and controllin'gthe work. V

i For. adjusting and initially setting-up the parts the slides l5 and I6 are adapted to be moved as a unit relative to the bed In and independently relative to one another. For'this purpose an adjusting screw 2| is provided being journaled at its outer end in a bracket 22 secured to an extension of the bed In. The inner threaded end of the screw 2! is received in a nut 23 journaled in the upper slide 16 and the screwZl has secured,

to its outer end eXteriorly of the bracket 22 a pilot or hand wheel 24. Clamps 25 are provided for securing the slides to one another for movement as a unit relative to the bed In, while clamps 26 maybe employedfor securing the lower slide IE to the'bed permitting the adjustment of the upper slide l6 relative thereto.

As seen in Figure 6, the operative peripheral face 21 of the regulating wheel 19 is of an irregular contour having a discharge opening 28 formed therein at one point thereof. Adjacent one side of the discharge opening 28 is a shallow cut-away portion 29 to permit the insertion of awork piece in the throat of the grinder. A gradual cam surface 30 extends from the loading portion 29 to a point-substantially at 3| from whence the periphof the, regulating wheel I9 is such as to permit the insertion of the work when the portion 29 thereof is opposed to the grinding wheel. Rotation of the regulating wheel in a clockwise direction eifects, through the cam portion 38, a. gradual feed of the work toward the grinding wheel to reduce same to the desired size. The concentric portion 3| next comes into play permitting a dwell in the feed of the work to allow the work and wheel to spark out and provide the desired finish thereon. The discharge opening 28 is subsequently aligned with the work whereupon gravity causes the work to roll down the inclined wall 32a and to be discharged from the grinding throat into a suitable receptacle therefor, and not shown in the drawings.

From the foregoing it will be noted that the work must be fed into the grinding throatat a definite point in the grinding cycle, namely: when the portion 29 of the regulating wheel- I9 is opposed to the grinding wheel at which time the throat is considerably enlarged over the final size of the work. For this purpose the mechanism illustrated in Figures '1 and 8 is provided which includes a chute or magazine 33 for the work delivering same to a feed slide 34 reciprocable in a housing 35 carried by bracket 36 'secured to or integral with the bed of the machine. The slide 34 terminates at itsforward end in a nose 31 for pushing a work piece off the platform 38 upon which it rested prior to the insertion within the grinding throat. An overhead spring pressed foot 39 cooperates with the slide for positioning subsequent work pieces on the platform 38- and preventing feeding of more than one piece at a time within the throat of the grinder. For reciprocating the feed slide 34 in one direction the regulating wheel l9 has secured to its adjacent face a cam 40 having the recessed portion 4|. Riding on the cam 48 is a roller 42can'ied by a pin 43 extending from the slide 34. A head is also connected to the pin 43 and .forms one abutment for a spring 45 which abuts on its other end with the outer wall of the housing .35.- The spring 45 maintains contactbetween the roller 42 and cam track 40 and effects the actual feeding of the work from the platform 32 into. the throat onto the work rest blade 28. I

As will be seen from Figure 6, the recessed portion 4| of the cam track 48 is in definite relation with the feeding portion 29 of the regulating wheel 21 so that they will each reach the grinding throat at the same time. The operation of the feeding mechanism is as follows: a work piece is normally positioned on the platform 38 being held against inadvertent disassociation therefrom by the foot 39 and has the nose 31 abutting one end thereof. As the wheel 40 rotates and the recessed portion 4| aligns with the roller 42 spring 45 urges the slide 34 forward causing the nose 31 to push the work piece from the platform 38 into the grinder throat. Simultaneously with this movement a shoulder 46 on the slide 34 and engaging the second work piece renders the foot 39 inoperative so that the said work piece may be ejected from the platform 38. As the roller rides out of the depression 4| the slide 34 is retracted and the foot 39 strips the work from the portion of the slide between its nose 31 and shoulderv 46 and deposits same on the platform 38 pending a repetition of the feeding cycle.

At a definite point during the grinding of the work the grinding wheel and work are reciprocated substantially axially of one another. For this purpose the grinding wheel spindle I2 is provided with a reduced portion 41. forming aconnection with antifriction thrust bearing 48 mounted within a cage or housing 49 reciprocable through a bearing 50 secured to the pedestal The thrust bearing cage 49 is held against rotative movement by a key 5| which, however, does not interfere with the reciprocation thereof and the consequent movement-of the grinding wheel spindle |2. The thrust bearing cage 49 has secured in its forward end a ball socket 52 receiving the ball end 53 of a hydraulic piston rod 54 which extends slidably through a bearing 55 extending from the bearing 59. The extended bearing 55 also forms one end or head of a cylinder 56 in which is enclosed a piston 51 secured to the piston rod 54. Enclosing the other end of the piston 56 is a head 58 having a flange59 extending beyond the cylinder56 through which passes bolts or screws, such as 60, employed for clamping the cylinder heads 50 and 58 to the opposite ends of the cylinder 56 for closing the said ends thereof. The bearing or head 55 is provided with a port 6| from which conduit or pipe 62 extends and the head 58 is similarly provided with a port 63. from which a conduit or pipe 64 extends. Also, threadedly, adjustably carried by the head 58 is'a stop screw 65 for engagement with the end of the piston rod 54 to limit the movement of the piston 51 in one direction.

The regulating wheel spindle I8 is provided with a reduced extension 66 on which is mounted a sleeve 61 having at one end a flange 68 and the other end 69 reduced and mounted within antifriction thrust bearing 19 held in place by screw cagell. Intermediate its ends the sleeve 61 has a bearing 12 on which is mounted a pair of cams 13 and 14. As seen in Figure 4, each of the cams is provided with a plurality of arcuate slots 15 through whichcap screws 16 extend. The inner end of the screw 16 enters the flange on the sleeve. 61 for movement therewith, and since the sleeve 61 is secured to the spindle, as by threads 11, the cams consequently move with the spindle l8. Enclosing the parts just described is a housing 18 secured as by screws or bolts 19 to the rear end of housing or head |1. Pivoted within the housing 18 at 19' is an arm 88bearing intermediate its ends a roller 8| riding on the peripheryof the earns 13 and 14. The upper surface of the arm 89 has a contact face 82 engaging the lower end of a sliding spool valve 83. The valve 83 has cannelures 84 and 85 intermediate its ends and a socket 86 in its upper end. Seated in the socket is a coiled spring 81 engaging upon its opposite end with the extension of an adjusting screw 88. The spool valve 83 is shiftable by the enlarged portion 89*of the earns 13 and 14 through a bushing 90 against the resistance of the spring 81. The bushing 98 ispressed into a valve cage 9| secured to the housing" by suitable fastening means extending through the flange 92 formed at the bottom thereof.

The casing 9| is provided with a plurality of ports 93, 94, and 96. The port 93 is connected by a suitable conduit to a hydraulic pressure source for conveying the pressure to the valve casing 9|. As shown in Figure 4, the pressure passes from the port 93 through cannelure 85 to the port 94 to which the one end of conduit 62 is secured for conveying the hydraulic pressure to the cylinder 56 and retracting the piston 51 to the position shown in Figure 3.- Thehydraulic medium ahead of thepiston-51 is exhausted through the port 63 and conduit 64 which conduit terminates at the port 95 in the valve casing 9|. The

exhaust medium in this instance is directed ,by the cannelure 83 to a port 91 which connects with the exhaust port 96 from which extends the exhaust conduit 98 to a suitable sump or tank, as is usual practice. As the high part of the cam 89 comes in contact with the roller M for shifting the valve 83 the pressure from the port 93 will be connected by the cannelure 84 with the port 95 for shifting the piston 5'! to the left, as seen in Figure 3. At this time the exhaust ahead of the piston 51 will be discharged through port IiI, conduit 62, port 94 and a port 99 connecting with the common exhaust port or duct 96. It will be understood that continued rotation of the cams I3 and I4 permits the spring 8'! to return the valve to the position shown as soon as the high part passes from under the roller 8 I.

Due to the arcuate slots 15 in the earns 13 and 14 they may be oscillated relative to one another about the axis of spindle I8 and clamped in this position by the bolts I6. This adjustment of the cams will extend the enlarged end 09 beyond that shown in solid lines in the drawings to the position shown in dotted lines at I00 in Figure 4. This would hold the valve spool 83 upwardly for a longer period of time and hold the piston to the left for a greater period of time, as should be well understood.

To control the rate of movement of the piston 51 in one or both directions and at the same time control the rate of reciprocation ofv the grinding wheel, the valve casing BI is provided with a pair of adjustable needle valves WI and I02, the former controlling the exhaust port 91 while the latter controls the exhaust port 99. If it is desired to have a slow travel of the grinding wheel in one direction and a rapid return in the other direction, it will only be necessary to completely open one of the valves IOI or I02 and adjust the other for limiting or controlling the exhaust through the remaining port.

When desired to cut out or eliminate reciprocation of the grinding wheel and itsspindle the following mechanism may be resorted to. By reference to Figure 4, it will be noted that the free end of the arm 80 is provided with a cam face I03 which is adjacent a screw I04 extending through the adjacent wall of the. housing 18. The locking nut I05 on the screw I04 is backed away and as soon as the high portions 89 of the cams I3 and 14 come into play the screw I04 is actuated to the left, as seen in Figure 4, to engage the cam face I03 thereby preventing movement of the valve 83 by the spring 81. By this construction the hydraulic pressure would be maintained against the right hand face of the piston, as seen in Figure 3, for holding same toward the left, without danger of movement thereof during grinding. I

What is claimed is:

1. In a grinding machine the combination of a bed, bearings on the bed, a grinding wheel spindle rotatably carried by the bearings, a grind ing wheel on the spindle, means for intermittently, axially reciprocating the spindle in opposite directions relative to its bearings, and means for regulating the rate of reciprocation of the spindle in one or both directions.

2. In a grinding machine the combination of a bed, a grinding wheel spindle rotatably carried thereby, a grinding wheel on the spindle, means for intermittently, axially reciprocating the spindle in opposite directions, means for regulating the rate of reciprocation of the spindle in one or both directions, and means varying the time element between intermittent reciprocations of the spindle.

3. In a centerless grinder the combination of a pair of opposed grinding and regulating wheels, a spindle for one of the wheels, hydraulic means for reciprocating said spindle, and means operable in timed relation with the rotation of the other wheel for controlling the energizing of, the spindle reciprocatingmeans. 1

4. In a centerless grinder the combination of a pair of opposed grinding and regulating wheels forming a grinding throat therebetween, a work rest blade withinthe throat supportinga work piece in simultaneous engagement with said wheels, means-for axially shifting the grinding wheel relative to the work, and means operable by the regulating wheel for intermittently energizing the grinding wheel reciprocating means. 5. In a centerless grinder the combination of apair of opposed grinding and regulating wheels forming a grinding throat therebetween, a work rest blade within the throat supporting a work piece in simultaneous engagement with said wheels, means for axially shifting the grinding wheel relative to the work-means operable by the regulating wheel for intermittently energizing the grinding wheel reciprocating means, and means for adjusting the rate of reciprocation in one or both directions. 1

6. In a centerless grinder the combination of a pair'oi opposed grindingand regulating wheels forming a grinding throat therebetweema work rest blade within the throat supporting a work piece in simultaneous engagement with said wheels, means for axially shifting the grinding wheel relative to the work, means operable-by the regulating wheel for intermittently energizing the grinding wheel reciprocating means, means for adjusting the rate of reciprocation in'one or both directions, and means for adjusting the control means to vary the time element between intermittent reciprocations of the grinding wheel.

1. In a centerless grinderthe combination of a pair of opposed grinding and regulating wheels forming a grinding throat therebetween, a work rest blade subtending the grinding throat supporting a. work piece in simultaneous engagement with the wheels, means for axially, intermittently reciprocating the grinding wheel relative" to the work, means for intermittently feeding a work piece to the work rest blade, and means carried by the regulating wheel for controlling and timing the intermittent reciprocations of the grinding wheel and the intermittent feeding of the work. Y

8. In a centerless grinder the combination of a pair of opposed grinding and regulating wheels,

a spindlefor each wheel,' a pistonon the end of the grinding wheel spindle, a cam on the'end of the regulating wheel spindle, a hydraulic medium for actuating the piston, 'a valve controlling the direction of flow of the medium, and means operated by the regulating wheel spindle ca'mzfor shifting the valve to effect reciprocation of the piston whereby the grinding wheel spindle is reciprocated in timed sequence with the rotation of the regulating wheel.

.9. In a centerless grinder the combination of a pair of opposed grinding and regulating wheels, a spindle for each wheel, a piston on the end of the grinding wheel spindle, a cam on the end of the regulating wheel spindle, a hydraulic medium for actuating the piston, a valve controlling the direction of flow of the medium, means operated by the regulating wheel spindle cam for shifting the valve to effect reciprocation of the piston whereby the grinding wheel spindle is reciprocated in timed sequence with the rotation of the regulating wheel, and means for controlling the rate of flow of the hydraulic medium to thereby control the rate of reciprocation of the grind ing wheel.

10. In acenterless grinder the combination of a pair of opposed grinding, and regulating wheels, a spindle for each wheel, a piston on the end of the grinding wheel spindle, a cam on the end of the regulating wheel spindle, a hydraulic medium for actuating the piston, a valve controlling the direction of flow of the medium, means operated by the regulating wheel spindle cam for shifting the. valve to effect reciprocation of the piston whereby the grinding wheel spindle is reciprocated in timed sequence with the rotation of the regulating wheel, means for controlling the rate of flow of the hydraulic medium to thereby controlv the rate of reciprocation of the grinding wheel, and means for varying the cyclic effect of the regulating wheel cam to adjust the time interval in the intermittent reciprocations of the grinding wheel spindle.

11. In a grinding machine the combination of abed, bearings supported by the bed, a spindle rotatably mounted in the bearings, a piston operatively connected with the spindle, an hydraulic medium for reciprocating the piston and consequently the spindle throughv its bearings, a valve for directing the hydraulic medium to opposite ends of the piston, yielding means for shiftingthe valve in one direction, and a rotatable cam'for shifting the valve in the other direction.

, 12. In a grinding machine the combination of a bed, bearings supported by the bed, a spindle rotatably mounted in the bearings, a piston operatively connected with the spindle, an bydraulic medium for reciprocating the piston and consequently the spindle through its bearings, a valve for directing the hydraulic medium to opposite ends of the piston, yielding means for shifting the valve in one direction, and a rotatable cam for shifting the valve in the other direction, said cam comprising a plurality of members adapted to be adjustedrelative to oneanother for varying the contour'of the cam and thereby varying the shifting of the valve.

13. In a grinding machine the combination of a bed, bearings supportedby the bed, a spindle rotatably mounted in the bearings, a piston operatively connected with the spindle, an hydraulic medium for reciprocating the piston and consequently the spindle through its bearings, a valve for directing the hydraulic medium to opposite ends of the piston, yielding means for shifting the valve in one direction, a rotatable camfor shifting the valve in the other direction, said. cam comprising a plurality of members adapted'to be adjusted relative to one another for varying the contour of the cam and thereby varying the shifting of the valve, and means controlling the rate of flow of the medium to thereby control the rate of movement of the piston and spindle.

14. In a mechanism ofv the class described for effecting an intermittent reciprocation of a spindle relative to its bearings the combination with a; spindleand bearings therefor, of a piston operatively connected with the spindle, an hydraulic medium for reciprocating the piston and consequently the spindle relative to its bearings, a valve for controlling the direction of flow of the medium for directing same to opposite ends of the piston, yielding means for shifting the valve in one direction, a cam for shifting the valve in the other direction, and means between the cam and valve for imparting a shifting movement to the valve in accordance with a shifting thereof by the cam.

15. In a mechanism of the-class described for effecting an intermittent reciprocation of a spindle relative to its bearings the combination with a spindle and bearings therefor, of a piston operatively connected with the spindle, an hydraulic medium for reciprocating the piston and consequently the spindle relative to its bearingsg a valve for controlling the direction of flow of the medium for directing same to opposite ends of the piston, yielding means for shifting the valve in one direction, a cam for shifting the valve in the other direction, means between the cam-and valve for imparting a shifting movement to the valve in accordance with a shifting thereof by the cam, said means being in the nature of a cam follower held in contact with the valve and cam by the yielding means operating on the valve, and means rendering the follower inoperative and holding the valve against movement against the yielding valve shifting means. a

16. In a mechanism of the class described for effecting an intermittent reciprocation of a spindle relative to its bearings the combination with a spindle and bearings therefor, of a piston operatively connected with the spindle, an hydraulic medium for reciprocating the piston and consequently the spindle relative to its bearings, a valve for controlling the direction of flow of the medium for directing same to opposite ends of the piston, yielding means for shifting the valve in one direction, a cam for shifting the valve in the other direction, and means between the cam and valve for imparting a shifting movement to 1 the valve in accordance with a shifting thereof by the cam, said means comprising an arm pivotally mounted at one end, a roller on'the other end contacting with the cam and the arm engaging with the valve, and a lock out screw adapted to hold the arm with its rollerout of 7 contact with the cam for thereby holding the valve against movement by its yieldable shifting means. 1'7. In a grinding machine of the class 'described the combination of a bed, a grinding wheel rotatably mounted on the bed, awork support adjacent the grinding wheel and adapted to support a work piece with its axis disposed parallel with the axis of the grinding wheel, means for effecting a cyclic approach and retraction of the work and grinding wheel to reduce the work to a definite size and form, means for effecting a single axial reciprocation in opposite directions between the work and grinding wheel during'the cyclic feed and retracting movements of the parts, and means for operatively connecting the feeding means and reciprocating means whereby the said single reciprocation is effected atthe same point during each cyclic feeding movement, said connecting means'being adjustable whereby the point in the feeding cycle at which the reciprocation takes place. may be varied.

FREDERICK S.- HAAS. 

